CN101929303A

CN101929303A - Electric actuator for driving a home automation screen

Info

Publication number: CN101929303A
Application number: CN2010102173365A
Authority: CN
Inventors: 埃里克·拉加德; 迪迪埃·梅内特里耶
Original assignee: Somfy SA
Current assignee: Somfy Activites SA
Priority date: 2009-06-23
Filing date: 2010-06-23
Publication date: 2010-12-29
Anticipated expiration: 2030-06-23
Also published as: RU2010125610A; EP2267330B1; US20100320855A1; FR2946997B1; ATE547642T1; EP2267330A1; RU2514594C2; FR2946997A1; US8253288B2; PL2267330T3; CN101929303B

Abstract

This electric actuator for driving a home-automation screen is provided with a spring brake (105) comprising a helical spring (130), a friction part (140) having a friction surface (141) against which the helical spring (130) bears radially. Said brake further comprises an inlet part (110) suitable for driving the spring in rotation in a direction reducing the contact force between the spring (130) and the friction part (140), and an outlet part (120) connected to the screen. While the screen is being lowered, the inlet part (110; 210) drives the spring (130; 230) in rotation with the contact force being decreased to the extent that the outlet part (120; 220) is released in rotation, without direct contact between the inlet part and the outlet part. The inlet part (110; 210) has at least two contact surfaces (113a, 113d; 213b, 217c) suitable for transmitting drive torque (CM) for raising the screen (2), by direct contact, to at least two corresponding contact surfaces (123a, 123d; 223b, 227a) of the outlet part (120; 220).

Description

Be used to drive the electric actuator of home automation screen spare

Technical field

The present invention relates to a kind of electric actuator that is used to drive home automation screen spare, described covering can be any one in the following type: spool shutter, curtain, curtain, door, projection screen or garage door.Actuator of the present invention is equipped with spring-loaded brake.The brake of the type more specifically is suitable for tubular motor.

Background technology

It is known using the helical spring brake at the actuator that is used for home automation screen spare, especially from patent document FR B 2610668 as can be known.In that part file, helical spring is installed on the friction means.At least one circle of spring radially compresses by a boring in the friction means.Each end of spring is formed with a protuberance, and described protuberance extends towards the inner radial ground of spring.Thereby each protuberance can be moved driving spring around its rotational.Input block, output block and spring are arranged to realize following power behavior especially: the action that comes from the input block that is positioned at first protuberance, one side causes spring to rotate on first direction.This rotation is unclamped output block, be that is to say that it trends towards reducing the peripheral envelope diameter of spring.Therefore, the frictional force between the boring in the friction means and the circle of spring reduces, thereby reduces the radial pressure between spring and the friction means.On the contrary, the action that comes from the output block that is positioned at the first protuberance opposition side cause spring in second direction, that is to say in the opposite direction and rotate.This rotates inaccessible output block, that is to say that it trends towards increasing the envelope diameter of the periphery of spring.Therefore frictional force between the boring in the friction means and the circle of spring increase.Same process is applicable to the radial pressure between spring and the friction means.In addition, on second direction, rotate, also unclamp output block simultaneously thereby input block also can act on the second protuberance driving spring of spring.Further, thus output block also can act on the second protuberance driving spring of spring to rotate on first direction.In this case, output block is perhaps relied at least with the elastic-friction of friction means and brakes by obturation.Therefore, the input block in the rotation makes the rotation of spring and output block become possibility, and simultaneously, the output block in the rotation stops the motion by output block caused.

The main brake of output block is therefore by realizing with the elastic-friction of friction means.Second phenomenon to the braking of output block contribution is arranged, just output block is in the friction at its guiding device place.This friction directly relates to the moment of torsion that puts on brake.When driving torque put on input block, input block put on output block by the protuberance of spring with power.Because this power is asymmetric about the axis of output block, it causes radial load, and this radial load causes output block to be moved up to it by its guiding device.That contact will be braked output block.When moment of torsion put on output block, described output block put on a protuberance of spring with power, and this power trends towards spring is kept static in rotation.As the reaction to this asymmetric power, radial load causes output block to be moved up to it by its guiding device.Therefore, in the design of traditional spring-loaded brake, have second braking torque, the main brake moment of torsion between that described second braking torque is added into spring and the friction means.Then, that second braking torque not only applies when covering rises but also when covering descends.

In patent EP-B-0976909, spring-loaded brake comprises: have the input block of two teeth, also have output block, spring and a friction means of two teeth.The driving torque that puts on input block is passed to output block by a tooth by a protuberance in the protuberance of spring, and this protuberance props up a tooth by output block.Because it is asymmetric putting on the power of output block, it causes putting on the radial load of described output block and therefore causes second braking torque.When moment of torsion put on output block, the phenomenon that occurs in the brake of FR-B-2610668 appearred being similar to.The tooth of output block props up a protuberance by spring, the inaccessible described spring of described protuberance.As the reaction to this asymmetric power, radial load causes output block to be moved up to it by its guiding device.

Described as in the example above traditional spring-loaded brake design, its method of operating stands the hardship of the defective in some structure.When actuator driving covering on the direction that descends, that is to say when the load torque that applies in the weight of output block by covering with come from input block driving torque that actuator applies on identical direction in, it is favourable that second braking torque is added into the main brake moment of torsion, because that will reduce the response time of brake, thereby make that installation is safer.Unfortunately, when covering rise, that is to say when the load torque that applies in the weight of output block by covering with come from input block driving torque that actuator applies opposite in, the existence of second braking torque is unfavorable especially, because brake is braked constantly, thereby need the motor of oversize.Motor not only needs to promote load, that is to say the moment of torsion that applies above load torque, and needs compensation second braking torque, because described second braking torque is added into load torque.

Summary of the invention

The present invention proposes a kind of electric actuator that is equipped with spring-loaded brake, and described spring-loaded brake improves the work of above-mentioned brake, also keeps the advantage of those brakes simultaneously.For the size of optimization motor, the present invention is devoted to eliminate second braking torque when promoting load.For this reason, the invention provides a kind of electric actuator that is used to drive home automation screen spare, described covering is arranged between open position and the fastening position and moves, and described actuator is equipped with spring-loaded brake, and described brake comprises:

Helical spring, described helical spring each end part is formed with protuberance separately, and described protuberance radially or axially extends with respect to the central axis of spring;

Friction means, described friction means have and are roughly columnar friction surface, helical spring at least one circle radially twelve Earthly Branches by described friction surface;

Input block, described input block is the motor-driven by actuator by this way, and be suitable for contacting, make driving spring rotate along the direction that can reduce the contact pressure between helical spring and the friction surface around the central axis of brake with at least one protuberance of spring;

Output block, described output block links to each other with covering and is suitable for contacting by this way with at least one protuberance of spring, makes driving spring rotate along the direction that can increase the contact pressure between helical spring and the friction surface around the central axis of brake.

In this actuator, when covering descended, under input block and situation that output block does not directly contact, the input block driving spring rotated, and makes contact pressure be reduced to the released degree of rotation of input block.According to the present invention, input block has at least two contact surfaces, and the driving torque that described contact surface is suitable for will being used to by direct contact promoting covering is passed to the contact surface of at least two correspondences of output block.

Covering produces load torque at output block, and described moment of torsion makes that producing second braking torque becomes possibility.As a result, this actuator is particularly suitable for vertically mobile covering, and the weight of described covering makes that producing above-mentioned load torque becomes possibility.This can be used for around pipe coiling baffle plate or be used for swinging garage door between horizontal level and vertical position.

Input block only directly contacts when covering rises with output block.Therefore, in decline, these two parts directly do not contact with transfer drive torque.In decline, input block is by a protuberance release brake in the protuberance that only acts on spring.Driving torque puts on that protuberance.There is not the transmission of power between input block and the output block.Output block is by another protuberance holding position of spring.As a result, the power that produces by load torque only puts on that protuberance, thereby driving spring can increase the direction rotation of the contact pressure between helical spring and the friction surface around the central axis edge of brake.

In this description, " directly contact " between two parts means that parts act on another parts, or the direct cooperation by complementary surface or be arranged on the cooperation of another parts between these surfaces or the combination by above-mentioned cooperation type rigidly by the dependence between the complementary surface.Directly contact can realize by the one or more contact surfaces that are arranged on output block, and such contact surface is to prop up thereon by complementary contact surface that input block is arranged or by the surface of the complementary surface of the intermediate member of input block promotion.In order to implement the present invention, must make moment of torsion transmit by at least two contact surfaces of output block.

Make and in rising, reduce the balance that second braking torque becomes possible driving torque, contact surface that can be by a plurality of series around the axis of the rotation of spring so that driving torque transmits in roughly balanced mode and realizes rapidly, thereby output block is not radially relatively stressed.The surface of these series can be arranged to reduce or eliminate the mode of the radial load that is caused around the axis of output block.For example, moment of torsion can transmit by two contact surfaces of output block, and described two contact surfaces are roughly the same and relative to angle ground each other about the axis of output block.This solution is easy to implement.

Advantageously, no matter be used to promote the direction of the driving torque of covering, the operation of brake is identical.This feature makes realization can be independent of the structure of covering and the multiduty actuator installed becomes possibility.For example, for the tubular type actuator that is installed in the coiling pipe, no matter covering is still reeled in one direction in the opposite direction, and the operation of actuator is identical.Whether the feasible scope of product and the possibility that is mounted for of being convenient to actuator rationalized of the operation of this symmetry of brake should install in special mode with respect to covering because need not to distinguish motor.

According to other favourable but non-essential aspect of the present invention:

Do not having under the situation of driving torque, output block puts on the protuberance of spring by this way with power, makes driving spring rotate along the direction that can increase the contact pressure between spring and the friction surface around the central axis of brake;

At at least one contact surface place, input block is reached with direct the contact by the rigid element as a protuberance in the protuberance of spring between the output block;

The structure of contact surface makes the balanced driving torque that promotes that transmits become possibility, thereby eliminates or reduce to be passed to the radial component of the power of output block with respect to the pivot center of spring significantly; And

Two contact surfaces of output block are relative to angle ground each other about the axis of output block.

Can be set to, when radial load puts on output block, output block is suitable for parts, contacts with parts that are anchored on or are integrally formed at friction means or input block specifically, described parts have and the different dynamic performance of the dynamic performance of output block, and described radial load only just can produce when covering descends.

When covering descended, described output block advantageously was suitable for following of the effect of the radial component of making a concerted effort of described load torque by being used for the centering member of described output block with respect to described input block centering.

Can be set to, output block is directed into respect to input block and rotates.Input block and output block be centrally aligned relative to each other.Input block and output block can by pass described parts the axle and centrally aligned.Axle be installed in input block or the output block in close-fitting mode and be mounted to can be at another parts, just in corresponding output block or input block, sliding.This centrally aligned is easy to reach and is compact.The sub-component that forms by input block and by output block is therefore with respect to friction means centrally aligned advantageously.This centrally aligned can be reached by output block or by input block.Preferably, sub-component is by the input block centrally aligned, because this can reduce the vibrations of brake significantly.

Description of drawings

Reading the following description just provide as example also with reference to the accompanying drawings, the present invention may be better understood, wherein:

Fig. 1 is the structural representation that combines the tubular type actuator of spring-loaded brake of the present invention of the present invention;

Fig. 2 is the exploded perspective view of spring-loaded brake, and this spring-loaded brake belongs to actuator shown in Figure 1;

Fig. 3 is the schematic cross-section that spring-loaded brake 2 shown in Figure 2 is operated in load is risen;

Fig. 4 is the schematic cross-section that spring-loaded brake 2 shown in Figure 2 is operated in load descends;

Fig. 5 is the schematic cross-section of spring-loaded brake operation in load is risen of prior art;

Fig. 6 is the exploded perspective view of second embodiment of spring-loaded brake, and this spring-loaded brake can be parts of actuator shown in Figure 1;

Fig. 7 is the exploded perspective view of different angles of some assembly of spring-loaded brake shown in Figure 6;

Fig. 8 is the schematic end view of observing along the arrow F of Fig. 6 and sectional view partly, and it has shown spring-loaded brake shown in Figure 6 operation in load is risen, and this output block that loads on brake produces the moment of torsion on the clockwise direction;

Fig. 9 is that the office that is similar to Fig. 8 is the schematic end view in cross section, and it has shown spring-loaded brake shown in Figure 6 operation in load descends, and this output block that loads on brake produces the moment of torsion on the clockwise direction;

Figure 10 is that the part that is similar to Fig. 8 is the schematic end view in cross section, and it has shown spring-loaded brake shown in Figure 6 operation in load is risen, the moment of torsion of the rising of load on the output block of brake produces counterclockwise;

Figure 11 is that the part that is similar to Fig. 8 is the schematic end view in cross section, and it has shown spring-loaded brake shown in Figure 6 operation in load descends, the moment of torsion of the decline of load on the output block of brake produces counterclockwise.

The specific embodiment

Fig. 1 diagram shows Rotary pipe type actuator 100, and it is intended to drive the pipe 1 of reeling with rotating manner, and the baffle plate 2 that is used for closing any opening O on the pipe 1 of reeling may be reeled to some extent.Actuator 100 driving tubes 1 rotate about the axis of rotation X-X in the upper opening portion horizontal arrangement.For example, opening O is provided in a side of the opening on the building wall.Actuator 100 has formed the roller shutter that motor drives after pipe 1 and the baffle plate 2.

Actuator 100 comprises by fixed cylinder pipe 101, motor and the transmission unit 102 be made up of motor 103, first order gearbox 104, spring-loaded brake 105, second level gearbox 106 and output shaft 107 are installed therein, output shaft 107 is outstanding at an end 101A of pipe 101, and drives the torus 3 that is constrained to managing 1 rotation.

The pipe 1 of reeling is coupled part about axis X-X and stationary pipes 101 rotations by means of two rotations.Being installed in bearer ring 4 near the excircle pipe 101 the end 101B relative with end 101A has formed first and rotates and be coupled part.Second rotation is coupled the other end that part is installed in pipe 1, and not shown.

Actuator 100 also comprises securing member 109, and it is outstanding and make actuator 100 can be anchored on framework 5 from end 101B.In addition, described securing member 109 is designed to sealed tube 101 and supports the control module 108 that is used to control to motor 103 power supplies.Described control module is by main power line 6 power supplies.

When 100 work of tubular type actuator, motor and transmission unit 102 are with rotating manner driving shaft 107, and it passes through torus 3 conversely with rotating manner driving tube 1.For example, when actuator 100 was installed in the roller shutter case, the rotation of axle 107 caused opening O alternately to open and to close.Therefore, baffle plate 2 in opening O, vertical moving between a high position of opening and the low level of closing.

Fig. 2 to Fig. 4 more specifically shows the structure of the spring-loaded brake 105 in first kind of embodiment of the present invention.As shown in Figure 1, the rotor of motor 103 drives the epicyclic train of first order gearbox 104.The cylinder 110 of three planetary epicyclic trains of carrying has also formed the input block of brake 105.Brake 105 comprises helical spring 130, and the circle of helical spring 130 is with axis X ₁₃₀Be the center, when brake 105 during in position as shown in Figure 1, axis X ₁₃₀Overlap with axis X-X.Described spring is installed in 141 inside, hole of friction means 140 with interference fit.In other words, the external envelope face 131 that the outer bus by its circle of spring 130 limits withstands the radial surface in hole 141, is tending towards thus spring 130 and parts 140 are fixed together by frictional force.

Each end of spring 130 forms from its circle towards axis X ₁₃₀And the protuberance 132a, the 132b that radially extend to spring inner.

Input block 110 is provided with two projection or " tooth " 111a and the 111b that embed helical spring 130.Each

projection

111a or 111b have and are suitable for the surperficial 133a of the first protuberance 132a that forms spring first end respectively and form face 113a or the 113b that the surperficial 133b of the second protuberance 132b of spring second end contacts.Surface 133a is arranged in such a way, and makes the active force that is applied on the surperficial 133a cause spring about axis X ₁₃₀The direction of the direction of rotation of spring was rotated when the edge was applied on the surperficial 133b with active force.

One of

tooth

111a or 111b active force on surperficial 133a or 133b is tending towards discharging brake, that is, so that the mode that the radial stresses between the friction surface in the external envelope face 131 of helical spring 130 and hole 141 reduces one of moves among protuberance 132a or the 132b.This active force from one of

tooth

111a or 111b is tending towards about axis X-X radial contraction spring 130 so that its external envelope emaciated face from the hole 141 surface.Therefore, parts 110 can act on the spring 130 with the contact force between the friction surface that reduces spring and hole 141.Afterwards spring can about with the central axis X of brake 105 ₁₀₅The axis X that overlaps ₁₃₀Rotate, when actuator 100 was in assembled configuration as shown in Figure 1, axis X 130 overlapped with axis X-X itself.As the X that parallels to the axis ₁₀₅When extension or measurement, direction or size are called as " axial ".When with axis X ₁₀₅Vertical and when intersecting, direction be known as " radially ".

The output block 120 of brake 105 is positioned at the position relative with input block 110.Output block is provided with two

flange

121a, 121c, and it also embeds in the helical spring 130.Flange 121a is provided with two grooves or step 122a, the 122b that is arranged in described flange both sides.Each

groove

122a or 122b are intended to hold one of

protuberance

132a, 132b of spring separately, and are limited by the surperficial 124a, the 124b that are suitable for contacting with surperficial 134a, the 134b of

protuberance

132a, 132b particularly.

Surface

134a and 134b are relative with surperficial 133a and 133b respectively.

Active force on one of surperficial 134a and 134b is tending towards

protuberance

132a and 132b divided to be opened, and the circle that causes spring 130 thus is with respect to axis X ₁₃₀Radially enlarge and increase the contact force between the friction surface in spring 130 and hole 141.This has caused the driving brake, that is, stop or energetically tripping spring 130 with respect to the rotation of parts 140.Therefore, radial stresses between helical spring external envelope face 131 and friction surface 141 increases, and keeps parts 120 static thus or about axis X ₁₀₅And axis X ₁₃₀With its big dynamic braking.

In order to make brake work, it is necessary having the gap, angle between the protuberance 132a of the tooth 111a of

input block

110 and 111b and spring and 132b.Similarly, protuberance 132a and the gap, angle between the 132b at flange 121a and spring also is necessary.The width of flange 121a is exactly to design for this purpose.In addition, the axial length L of 111a, 111b and 121a part ₁₁₁Or L ₁₂₁The axial length L of being a bit larger tham spring ₁₃₀

Output block 120 also is provided with the tooth 129 of one group of formation and second level gearbox 106 interfaces.

Output block 120 with respect to necessity of input block 110 between two parties by realizing with the axially outstanding axle 118 of the same side of output block 120 with respect to input block.Described axle 118 serves as the guiding device that is used to guide output block by means of the hole 128 that is set to pass described output block center.

More specifically manifest as from Fig. 3 to Fig. 4, the load L that is made of baffle plate 2 can be regarded as being fixed in output block 120 by element 1,3,106 and 107, shown in the vertical dotted line among Fig. 3 and Fig. 4.

The weight of load L applies moment of torsion C on output block 120 _L, moment of torsion C _LBe tending towards causing output block 120 along the clockwise direction among Fig. 3 and Fig. 4 about axis X ₁₀₅Rotate.

With reference to X ₁₂₀The central axis of indication output block 120, when brake is in assembled configuration, this axis and axis X ₁₀₅Overlap.

When rising load L, shown in diagram among Fig. 3, by moment of torsion C _LThe output block 120 that causes clockwise rotation in Fig. 3 is stoped by input block 110.Moment of torsion C that input block 110 is produced by motor and that increase by the efficient of first order gearbox 104 _MIn Fig. 3, drive with rotating manner with counter clockwise direction.Two projection 111a of

input block

110 and 111b are about overlapping axis X ₁₀₅And the X-X rotation contacts with the face 123a or the 123b of the flange of output block up to one of projection 111a or 111b.So another

projection

111b or 111a also enter with one of the face 123c of the second flange 121c of output block or 123d and contact.Therefore, driving torque C _MBe transferred to output block by two set of contact surfaces, this two set of contact surface is formed on about axis X ₁₀₅Axis X with output block ₁₂₀Between face 113a that the diagonal angle is relative each other and 113d and face 123a and the 123d, cause being applied to the moment of torsion C on the output block 120 thus _MConsequent radial component be reduced or eliminate.Driving torque C _MWith load torque C _LDirection opposite.Face 123a and 123d have constituted the contact surface of output block 120.

The equilibrium of forces that is born for output block 120 shown in Fig. 3.Load torque C _LBy power F _1aAnd F _1bBalance, power F _1aAnd F _1bCause and cause by the surperficial 113a of the tooth 111a that withstands each other and the surperficial 123a of flange 121a respectively by the surperficial 113d of the tooth 111b that withstands each other and the surperficial 123d of flange 121c.These two power F _1aAnd F _1bRepresent to be used to overcome load torque C in the mode of power _LNecessary driving torque C _MBecause these two power F _1aAnd F _1bBasically big or small identical and basically about the central axis X of output block ₁₂₀Symmetry, the moment of torsion C of output block 120 _MThe radial component of making a concerted effort be inappreciable, or even zero.Should be noted that in this configuration the axle 118 of the input block that output block can be placed in the middle is not contacted with the hole 128 of output block, and its reason is that above-mentioned radial component of making a concerted effort is inappreciable.

For the load that raises, since the remaining frictional force between the friction surface in the external envelope face 131 of spring and hole 141, moment of torsion C _MMust be greater than load torque C _LMoment of resistance sum with tripping spring.The startup stage, the moment of torsion C that will apply _MMust be bigger, because, must overcome stiction in order to discharge brake 105.Therefore, in case drive flange 121a with rotating manner, projection 111a just acts on one of protuberance of spring, and in this example, this protuberance is the protuberance 132a that is contained among the groove 122a.

When load L is lowered, shown in diagram among Fig. 4, not to stop by input block but stop by spring 130 along right handed output block among Fig. 4.Therefore, load torque is pressed in flange 121a on one of

protuberance

132a or 132b, in this example, promptly is protuberance 132a.Such effect is radially to enlarge the circle of spring 130 to drive brake 105, as mentioned above.Be applied to the moment of torsion C on the surperficial 134a of protuberance 132a by flange 121a _LEfficient by second level gearbox 106 strengthens.Protuberance 132a is bonded among the groove 122a.Driving torque C _MWith load torque C _LDirection identical.

It shown in Fig. 4 the equilibrium of forces of output block.Load torque C _LBy two power F _2aAnd F _2bBalance.The first power F _2aCorresponding to the face 134a of the protuberance 132a of spring 130 reaction force to the bearing surface 124a of groove 122a.Because the described first power F _2aCan not full remuneration load torque C _L, output block 120 is tending towards with respect to aforesaid carrying configuration perpendicular to axis X ₁₀₅Move, begin to contact with its guiding device up to output block, guiding device is by being fixed in input block 110 or forming with the axle 118 of input block 110 for one.Be used to guide the hole 128 of output block therefore to begin to contact with axle 118, producing afterwards can balanced load moment of torsion C _LThe second radial load F _2bMove down in the process the described second power F in load _2bProduce frictional force.This frictional force has been braked load and has been added into the braking torque of spring.Therefore, it helps the reaction of brake.The response time of this brake is faster than the response time of the brake that does not have described frictional force.

Should be noted that embodiment hereto, with respect to rubbing device 140 self-centerings, 141 in the envelope surface (not shown) of cylindrical web and the rubbing device matches input block 110 by means of cylindrical web.Therefore, aforesaid power F _2bBetween input block 110 and rubbing device 140, can cause an equivalent force (not shown).Described equivalent force participates in the secondary braking moment of torsion and helps the reaction of brake.

In order to reduce load, it is necessary discharging brake.For this reason, driving torque C _MDrive the projection 111a and the 111b of input block 110 with rotating manner, projection 111b is driven up to it by described driving torque and begins face 133b adjacency with the protuberance 132b of spring 130.By this action, by means of load torque C _L, spring 130 is released and output block 120 can rotate.Not directly contact of

parts

110 and 120 afterwards.

If the coiling direction of load is opposite, operate identical.Therefore, the operation of brake is symmetrical, and for it, because the performance of brake is identical, it can more easily be installed, and no matter how no matter the ascent direction of actuator, that is, be used to promote the driving torque C of covering 2 _MDirection why.

Fig. 5 shows conventional prior art spring-loaded brake, and more specifically, how it works in uphill process.The parts that are similar to brake 105 of the brake shown in Fig. 5 use similar reference number to deduct 100.For the brake of the sort of type, output block is not designed to the load torque in the balance uphill process.Output block 20 only is provided with a protuberance 21a.In uphill process, operate similar to the operation of the brake 105 that disposes shown in Fig. 3.Driving torque C _MDriving projection 11a with rotating manner begins to contact with the face 33a of the protuberance 32a of spring 30 up to described projection.The opposite face 34a of protuberance is by means of load torque C _LEngage with the face 23a of the flange 21a of output block 20.Therefore, driving torque is transferred into output block 20 by the protuberance 32a of spring 30.

In above-mentioned embodiments of the present invention referring to figs. 1 to Fig. 4, contacting between the face 123a of face 113a of driving torque by input block 110 and output block 120 directly is sent to output block 120, and the spring protuberance is retracted in the set for this purpose groove 122a afterwards.This makes it can realize better moment of torsion transmission and can make parts bear less power.

In brake shown in Figure 5, load torque C _LCan not be sufficiently protuberance 32a by spring bear with the described moment of torsion of balance, and therefore on output block 20, produced radial load.Radial load causes output block to move up to it contacting with its guiding device, and guiding device is formed by the hole in the rubbing device 40 41.Output block 20 has cylindrical web, and its external envelope surface 25 makes it realize that in hole 41 guiding becomes possibility.Therefore, load torque power F ' at first by contacting with the protuberance 32a of spring 30 corresponding to flange 21a _1aSecondly balance is by contacting the power F ' that causes by output block 20 with hole 41 in the rubbing device _1bBalance, Given this, in uphill process, output block 20 has the relative velocity of relative rubbing device 40, in load ascending motion process, described power F ' _1bProduced frictional force.In order to promote load L, so driving torque C _MMust be greater than the load torque C of described frictional force _LDischarge the necessary moment of torsion sum of starter during with startup.Therefore, described frictional force influences determining of motor dimension unfriendly, because, in order to compensate by power F ' _1bThe extra frictional force that causes, described motor must be stronger.

In order to reduce load, class of operation is similar to the operation of brake of the present invention shown in Figure 3.Yet equilibrium of forces is similar to balance shown in Figure 5 more.The frictional force braking of the guiding device that load forms by the braking torque of spring and by the hole in the output block 41.

Fig. 4 and Fig. 5 show the guiding device that two kinds of different being used to guide output block 20 or 120.In Fig. 4, with respect to input block 110 guiding output blocks 120.Input block 110 is also placed in the middle with respect to friction means 140.In Fig. 5, with respect to fixing friction means 40 guiding output blocks 20.Test has demonstrated under the situation of Fig. 4 brake 105 and can work better.Output block is with respect to the vibration that can reduce brake between two parties of input block.

Fig. 6 to Figure 11 shows second kind of embodiment of brake.Operating principle approaches first kind of embodiment.The reference number of these parts is similar to the reference number of first kind of embodiment, adds 100.

The output of the epicyclic train of first order gearbox 104 drives the parts 210 of the input that forms brake 105 with rotating manner.Input block 210 is provided with the polygon shaft 219 that is intended to receive and send from the moment of torsion of gearbox 104.Brake 105 comprises helical spring 230, and its circle is around axis X ₂₃₀Centering, when brake 105 in the position shown in the figure 1 the time, axis X ₂₃₀Overlap with axis X-X.When the actuator 100 of the brake 105 that comprises this second kind of embodiment in the configuration of assembling the time, axis X ₂₃₀And the central axis X of axis X-X and brake 105 ₁₀₅Overlap.

Spring 230 is installed in 241 inside, hole of rubbing device 240 in the mode of interference fit.In other words, the external envelope face 231 of spring 230, this enveloping surface is limited by the outer bus of its circle, withstands the radial surface in hole 241, is tending towards thus by frictional force spring 230 and parts 240 being fixed together.

Each end of spring 230 forms from its circle towards axis X ₂₃₀And the protuberance 232a, the 232b that radially extend to spring inner.

Input block 210 is provided with protuberance 232a and the projection between the 232b or " tooth " 211a that embeds helical spring 230.Described tooth 211a has two and is suitable for respectively with the surperficial 233a of the first protuberance 232a that forms spring first end and forms face 213a or the 213b that the surperficial 233b of the second protuberance 232b of spring second end contacts.Surface 233a is arranged in such a way, be applied to this lip-deep active force cause spring along and when being applied on the surperficial 233b when active force the direction of the direction of rotation of spring about axis X ₂₃₀Rotate.

The active force of tooth 211a on surperficial 233a or 233b is tending towards discharging brake, that is, along the direction of the radial stresses minimizing between the friction surface in the external envelope face 231 that makes helical spring 230 and hole 241 about axis X ₂₃₀And X ₁₀₅Drive protuberance 232a or 232b with rotating manner.The active force from tooth 211a on one of

face

233a or 233b is tending towards about axis X-X radial contraction spring 230 so that its external envelope emaciated face from the hole 241 surface.Therefore parts 210 can act on the spring 230 with the contact force between the friction surface that reduces spring and hole 241.

The output block 220 of brake 105 is positioned at relative with input block 210.Output block is provided with two the flange 221a, the 221c that also embed in the helical spring 230.Each flange is provided with groove or step 222a, the 222b of one of each

protuberance

232a, 232b of being intended to hold spring 230.Each

groove

222a or 222b are limited by the surperficial 224a, the 224b that are suitable for contacting with surperficial 234a, the 234b of

protuberance

232a, 232b particularly.234a is relative with

surperficial

233a and 233b respectively with 234b on the surface.

Active force on one of

surperficial

234a and 234b is tending towards

protuberance

232a and 232b are moved towards each other, and the circle that causes spring 230 thus is with respect to axis X ₂₃₀Radially enlarge and increase the contact force between the friction surface in the external envelope face 231 of spring 230 and hole 241.This has caused the driving brake, that is, stop or energetically tripping spring 230 with respect to the rotation of parts 240.Therefore, the radial stresses between helical spring external envelope face 231 and friction surface 241 increases.

In addition, each

flange

221a, 221b of output block 220 are provided with

ledge

226a, 226b, and it extends axially to input block, and in case assembled brake 105, and it is suitable for being contained in respectively among banana-shaped groove 216c, the 216d in the input block 210.Described

ledge

226a and 226b are designed and sized to and are arranged so that

face

213b, 213a as the tooth 211a of input block 210 with the face 223b of flange 221b, the 221a of output block 220, when 223a contacts, and their

face

227a, 227b contacts with one of

inner face

217c, 217d of limiting

corresponding groove

216c, 216d respectively.

Fig. 8 and Figure 10 show two kinds of possible configurations of brake 105.The size of

groove

216c, 216d is defined as, make outside aforementioned two kinds of configurations,

ledge

226a, 226b not with any abutment of groove.

For brake can be worked, it is necessary having the gap, angle between the protuberance 232a of the tooth 211a of input block 210 and spring and 232b.Similarly, protuberance 232a and the gap, angle between the 232b at

flange

221a and 221b and spring also is necessary.The width of tooth 211a is exactly to design for this purpose.In addition, the axial length L of 211a, 211b and 221b part ₂₁₁Or L ₂₂₁The axial length L of being a bit larger tham spring ₂₃₀

Output block 120 is realized by axle 270 between two parties with respect to necessity of input block 210.Described axle engages in the centre bore 218 of input block 210.An axle part of 270 is outstanding from the side identical with output block 220.

Fig. 8 to Figure 11 shows brake 105 and how to work.Fig. 8 and Fig. 9 are corresponding to the covering of reeling on axle 1 along clockwise direction in described figure.Fig. 8 shows the load of rising, and Fig. 9 shows the load of reduction.Figure 10 and Figure 11 are corresponding to the covering of reeling on axle 1 in the counterclockwise direction in these figure.Figure 10 shows the load of rising and Figure 11 shows the load of reduction.

At first, the operation of the brake configuration with respect to first covering-coiling is made an explanation, that is, in Fig. 8 and Fig. 9, reel along clockwise direction.

Acquiescently, the weight of load L applies moment of torsion C on part 220 _L, this moment of torsion promptly is flange 221b with one of

flange

221a or 221b in this example, presses to one of

protuberance

232a or 232b, promptly is protuberance 232b in this example, as shown in Figure 9.Such effect is radially to enlarge the circle of spring 230 and start brake 105, as mentioned above.Be applied to the moment of torsion C on the surperficial 234b of protuberance 232b by flange 221b _LEfficient by second level gearbox 106 strengthens.This moment of torsion is illustrated by the vector related with flange 221b.Protuberance 232b is afterwards in being bonded on groove 224b.

When promoting load L, as shown in Figure 8, moment of torsion C that input block 210 is produced by motor and that increase by the efficient of first order gearbox 104 _MDrive with rotating manner.The projection 211a of input block 210 rotation afterwards is up to its flange 221b contacting at the interface between

surperficial

213b and 223b with output block.For the load that raises, moment of torsion C _MMust be greater than moment of torsion C _LAnd because the moment of resistance sum of the tripping spring that the remaining frictional force between the friction surface in the external envelope face 231 of spring and hole 241 forms.Moment of torsion C _MBy the dotted line vector representative related with input block.

The startup stage, the moment of torsion C that will apply _MMust be bigger, because, must overcome stiction in order to discharge brake 105.In order to discharge brake 105, when flange 221b was driven with rotating manner, projection 211a acted on the protuberance 232b that is contained among the groove 222b.Driving torque C _MBe sent to output block 220 by dual contact from input block 210.On a side, the face 213b of projection 211a withstands the face 223b of flange 221b.And along diagonal relatively, the inner face 217c of groove 216c withstands the face 227a of ledge 226a.Therefore, load torque C _LBy in the support of the part 211a of a side and 211b and the directed force F that causes in the part 216c and the support between the 226a of opposite side _1aAnd F _1bBalance.Because these two power F _1aAnd F _1bBasically big or small identical and basically about the central axis X of output block ₁₂₀Symmetry, the moment of torsion C of output block 220 _MThe radial component of making a concerted effort be inappreciable, or even

zero.Face

223b and 227a have constituted the contact surface of output block.

When reducing load L, shown in diagram among Fig. 9, output block 220 is not to be stopped by input block 210 but stopped by spring 230.Therefore, load torque C _LFlange 221a is pressed on one of

protuberance

232a or 232b, in this example, promptly is protuberance 232b.Such effect is to cause radially enlarging the circle of spring 230 and start brake 105, as mentioned above.

Be applied to the moment of torsion C on the surperficial 234b of protuberance 232b by flange 221a _LEfficient by second level gearbox 106 strengthens.Protuberance 232b is bonded among the groove 222b.Driving torque C _MWith load torque C _LDirection identical.Equilibrium of forces is different from the balance in the lifting process.Load torque C _LBy power F _2aAnd F _2bBalance.The first power F _2aThe reaction force that stops load corresponding to the interface place of spring between the bearing surface 224b of the groove 222b of the flange 221b of the face 234b of the protuberance 232b of spring 230 and output block.Because the described first power F _2aCan not compensating load moment of torsion C _L, output block 220 is tending towards rotating with respect to aforesaid braced structures, contacts with its guiding device up to output block, and this guiding device is by being fixed in input block 210 or forming with the axle 270 of input block 210 for one.Be used for therefore beginning to contact with axle 270 with respect to the hole 228 of axle 270 guiding output blocks 220, producing thus can balanced load moment of torsion C _LThe second power F _2bThis power is with respect to axis X ₂₂₀Be radially.Move down in the process this second power F in load _2bProduce frictional force.This frictional force has been braked load and has been added into the braking torque of spring.Therefore, it helps the reaction of brake.The response time of this brake is faster than the response time of the brake that does not have this frictional force.

Should be noted that embodiment hereto, with respect to rubbing device 240 self-centerings, the envelope surface (not shown) of cylindrical web matches with the hole 241 of rubbing device input block 210 by means of cylindrical web.Therefore, aforesaid power F _2bBetween input block 210 and friction means 240, produce the equivalent force (not shown).This equivalent force participates in the secondary braking moment of torsion that helps the brake reaction.

In order to fall load, it is necessary discharging brake.For this reason, driving torque C _MThe projection 211a that drives on the input block 210 with rotating manner begins to withstand the face 233a of the protuberance 232a of spring 230 up to it.By this action, spring 230 is released, and by means of load torque C _L, output block 220 can rotate, because not directly contact of

parts

210 and 220.

Operating in shown in Figure 10 and Figure 11 of brake during second kind of coiling disposes.

In lifting process, as shown in figure 10, load torque C _LBy at first by contacting between the face 223a of the face 213a of tooth 211a and flange 221a cause, secondly by the power F that causes that contacts between the face 227b of the inner face 217d of groove 216d and ledge 226b _1aAnd F _1bBalance.Because these power F _1aAnd F _1bBe balance, the moment of torsion C on output block 220 _MThe radial component of making a concerted effort be inappreciable.Therefore motor must be carried the loading moment C greater than the moment of resistance of only having added brake _LDriving moment, this moment of resistance is caused by the frictional force between spring 230 and the rubbing device 240.There is two stage braking moment very little or that do not produce by the frictional force between output block 220 and its axis of guide 270.

Face

223a and 227b have constituted the contact surface of output block.

In the process that reduces, loading moment C _LBy power F _2aAnd F _2bBalance.The first power F _2aThe reaction force that stops the spring 230 of load L corresponding to the interface place between the bearing surface 224a of the face 234a of the protuberance 232a of spring 230 and the groove 222a among the flange 221a.The second power F _2bCorresponding to when part 210 when 220 directly do not contact, the local power at the axis of guide 270 places of output block 220.This friction has produced the radial load of deceleration loading.Therefore, brake response is rapidly because the two stage braking moment of torsion no longer becomes insignificant.

These two kinds of embodiments have been described tripping spring, and its end is folding to spring inner.Certainly, described end can be outside folding to described spring.Another modification comprises the central axis folded end that is parallel to spring.On the both sides of spring, extend axially after the protuberance, simultaneously, extend to center position away from spring.

In addition, spring-loaded brake does not have special requirement must be contained between the two-stage gearbox.It can be arranged in the output of motor or output place of gearbox.

Claims

1. electric actuator (100) that is used to drive home automation screen spare (2), described covering (2) is arranged between open position and the fastening position moves, and described actuator is equipped with spring-loaded brake (105), and described brake comprises:

Helical spring (130; 230), each end of described spring is formed with separately protuberance (132a, 132b; 232a, 232b), described protuberance is with respect to the central axis (X of described spring ₁₃₀X ₂₃₀) radially or axially extend;

Friction means (140; 240), described friction means has and is roughly columnar friction surface (141; 241), at least one circle of described spring radially twelve Earthly Branches by described friction surface;

Input block (110; 210), described input block is driven by the motor (103) of described actuator by this way, and is suitable at least one protuberance (132a, 132b with described spring; 232a, 232b) contact, make to drive the central axis (X of described spring around described brake ₁₀₅) rotate along the direction that can reduce the contact pressure between described helical spring and the described friction surface;

Output block (120; 220), described output block links to each other with described covering (2) and is suitable at least one protuberance (132a, 132b with described spring; 232a, 232b) contact by this way, make to drive the described central axis (X of described spring around described brake ₁₀₅) rotate along the direction that can increase the contact pressure between described helical spring and the described friction surface;

In described actuator, when described covering descends, described input block (110; 210) drive described spring (130; 230) rotate, under described input block and situation that described output block does not directly contact, described contact pressure is reduced to described output block (120; 220) the d/d degree of rotation;

Wherein, described input block (110; 210) have at least two contact surfaces (113a, 113d; 213b, 217c), described contact surface is suitable for will being used to promote by direct contact the driving torque (C of described covering (2) _M) be sent to described output block (120; The contact surface of at least two correspondences 220) (123a, 123c; 223b, 227a).

2. no matter electric actuator according to claim 1 wherein, is used to promote the described driving torque (C of described covering (2) _M) direction how, the behavior of described brake (105) is identical.

3. according to a described electric actuator in claim 1 or 2, wherein, there be not under the situation of driving torque described output block (120; 220) power is put on by this way described spring (130; 230) described protuberance (132a, 232b) makes to drive the described central axis (X of described spring around described brake ₁₀₅) along increasing described spring and described friction surface (141; The direction of the described contact pressure 241) is rotated.

4. according to a described electric actuator in claim 1 or 2, wherein, at least one contact surface place, described input block (110; 210) with described output block (120; 220) the described direct contact between relies on spring (130 as described; 230) described protuberance (132a, 132b; 232a, 232b) in the such rigid element of a protuberance realize.

5. according to a described electric actuator in claim 1 or 2, wherein, described contact surface (113a, 113d, 123a, 123d; 213b, 223b, 217c, 227a) structure make the described lifting driving torque of balance (C by this way _M) transmission become possibility, make to eliminate or reduce significantly being sent to described output block (120; 220) power with respect to described spring (130; Axis (the X of described rotation 230) ₁₀₅) radial component.

6. according to a described electric actuator in claim 1 or 2, wherein, described output block (120; 220) described two contact surfaces (123a, 123d; 223b, 227a) about the described central axis (X of described output block ₁₂₀, X ₂₂₀) relative diagonally each other.

7. according to a described electric actuator in claim 1 or 2, wherein, when radial load puts on described output block (120; 220) time, described output block is suitable for the parts (118 different with described output block with dynamic performance; 270), specifically with described friction means (140; 240) or described input block (110; 210) fastening or integrally formed parts contact, and wherein said radial load only just can produce when described covering (2) descends.

8. according to a described electric actuator in claim 1 or 2, wherein, when described covering (2) descends, described output block (120; 220) be suitable at described load torque (C _L) the effect of the radial component of making a concerted effort under against being used for described output block with respect to described input block (110; 210) the centering member (118 of centering; 270).

9. according to a described electric actuator in claim 1 or 2, wherein, described output block (120; 220) be directed into respect to described input block (110; 210) rotate.

10. according to a described electric actuator in claim 1 or 2, wherein, by described input block (110; 210) with by described output block (120; 220) sub-component of Xing Chenging is with respect to described friction means (140; 240) centrally aligned.